US10520074B2 - Scissor gear assembly - Google Patents

Scissor gear assembly Download PDF

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Publication number
US10520074B2
US10520074B2 US15/745,767 US201615745767A US10520074B2 US 10520074 B2 US10520074 B2 US 10520074B2 US 201615745767 A US201615745767 A US 201615745767A US 10520074 B2 US10520074 B2 US 10520074B2
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Prior art keywords
gear
springs
main gear
spring
scissor
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US15/745,767
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US20180216716A1 (en
Inventor
Steven Van Lieshout
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VCST INDUSTRIAL PRODUCTS bvba
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VCST INDUSTRIAL PRODUCTS bvba
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/125—Adjustment of backlash during mounting or assembly of gearing

Definitions

  • the invention relates to a scissor gear assembly comprising:
  • a scissor gear assembly is well known in the industry and often used in combustion engines for driving cam shafts, balancer shafts, fuel injection pumps or air compressors to prevent rattling noise because of load reversals and/or crank torsional vibrations.
  • the scissor gear comprises a main and an auxiliary gear rotatable on a mutual axis and in rotation direction connected by a resilient member.
  • the resilient member can be a spring with an annular shape.
  • a scissor gear according to the preamble of claim 1 is known from DE102011115692A1.
  • the spring is selected in such a way that the negative torque due to load reversals and crank vibrations are eliminated.
  • the known scissor gear assembly has contact with both the driving flank and coast flank of its mating gear and because of this rattling is prevented. Especially, the rattling noise at low rpm for instance at idling is noticeable and not wanted.
  • the advantage of a flat annular spring compared with a coiled wire compression or coiled wire tension spring is the compact size in axial direction of the scissor gear assembly. This way the body of the scissor gear assembly can be kept thin so it does not need much engine space.
  • the spring load generated by opening or closing the annular spring can be easily transferred from the main gear to the auxiliary gear without creating significant tilting. This because the forces are in planes with relative small offset.
  • the spring ends can be positioned in the assembly such way that the spring forces are almost perfectly tangential to the rotation direction of the gear and the spring forces will deliver optimal spring torque. With a small interruption, the spring forces will give no or relative small bending torque in the fixation of the main gear and the fixation of the auxiliary gear. This way the spring fixation can be designed relatively small and the spring section can be designed small towards the ends to have maximum spring stroke.
  • the annular spring can be easily produced with fine blanking out of soft material. After the blanking process the annular spring needs to be hardened and tempered to a martensitic microstructure to get the desired spring properties.
  • An alternative heat treatment is austempering to a bainitic microstructure. The latter gives in general smaller heat distortion.
  • annular spring with only one interruption makes it often impossible to provide the main gear with holes for multiple bolts for axial clamping or mounting the gear to an axle or flange. This way applications of such a scissor gear are limited to situations where the fixation to an axle or a flange is with a central bolt or to situations without bolts.
  • auxiliary gear should be fixed in axial direction to the main gear in such a way that the fixation is effective, non-expensive and requires no or a little space.
  • the object is to provide a scissor gear assembly that does not have the disadvantages of the known gear assembly described above. More particularly, the object is to provide a scissor gear assembly having an improved axial fixation of the auxiliary gear to the main gear.
  • the scissor gear assembly according to the invention is characterized in that both of the ends of the springs in axial direction hook behind a hook attached to the main gear.
  • the main gear has a central hole and viewed in axial direction this central hole and the surface within the planar annular spring do not overlap each other.
  • a preferred embodiment of the scissor gear assembly according to the invention is characterized in that the main gear has a circular collar which is in contact with the inner surface of the toothed ring and is interrupted at locations where the springs extend inside the toothed ring, wherein the hooks are part of the side walls of the collar bounding the interruptions.
  • the connection between the gears needs less space.
  • the advantageous feature of a main gear having a collar can also be used in a scissor gear assembly having an other axial fixation known by somebody skilled in the art than the one described above for instance a retaining clip or a rotational bayonet lock.
  • a further preferred embodiment of the scissor gear assembly according to the invention is characterized in that the springs each have a shape of a half circle, at the ends of the circle there are arms extending in radial direction towards the middle of the circle.
  • Such a spring has an optimal characteristic for the purpose it is designed for.
  • this advantageous feature of the springs having a shape of a half circle it is noticed that this feature can also be used in a scissor gear assembly having an other axial fixation known by somebody skilled in the art than the one described above.
  • the scissor gear assembly according to the invention can be narrow and does not require a large springs that needs high investment for tooling to prevent distortion during heat treatment or that needs post machining due to distortion after heat treatment.
  • the springs of the assembly according to the invention should not be too slender that it will become instable because of lateral-torsional buckling or that the eigenfrequencies are becoming too low in the range of engine vibrations.
  • the main gear and the auxiliary gear rotatable positioned on a mutual axis need a minimum radial play. This to absorb geometrical and dimensional tolerances and to guarantee a minimum oil film.
  • the springs can be placed uniformly distributed over the gear around the mutual axis so the spring forces of the multiple springs are eliminating each other.
  • the auxiliary gear Upon rotation of the scissor gear assembly in mesh with another gear, the auxiliary gear will always be forced away from the gear in mesh because of the radial tooth force independent from the rotational position of the scissor gear assembly. This way the radial play will not affect the distance between the auxiliary gear and the gear in mesh during rotation. So, the multiple annular spring solution will not give a tooth to tooth transmission error nor will this solution give reasons for additional high frequency noise.
  • the individual springs are relative small and relative stiff in axial direction.
  • the eigenfrequencies of such small spring is much higher than a single large annular spring and can be kept above critical engine vibration frequencies.
  • Holes for fixing the scissor gear assembly to an axle or flange can be provided.
  • the bolds can be positioned through the central area of the annular spring or in the space formed between the uniformly distributed springs.
  • the relative small springs can be easily produced for instance with fine blanking without high tool invest. Because of the relative small size, distortion because of heat treatment is limited so the parts do not need post-machining or do not need expensive tooling and equipment for press hardening.
  • the relative small springs can be made from relative thick sheet (2 to 4 mm), so the annular spring will be relative stable and not sensitive for lateral torsional buckling.
  • the eigenfrequencies will be relative high and can be kept above the engine vibrations frequencies so resonance of the spring can be prevented.
  • the rotational speed and the torsional vibration of the shaft where the scissor gear assembly is mounted on will have less effect on the resulting spring force. Because the spring is completely placed radial outward the rotation axis, the centrifugal forces will force the complete spring outwards instead of opening the spring ends. So spring force is less dependent from rotational speed.
  • the spring ends have connection means for connecting the spring to the main gear and the auxiliary gear.
  • the connection means can be a pin, a hook or an abutting surface transferring the spring force from the main gear to the auxiliary gear.
  • Additional connection means can be provided to make assembly or transportation prior to mounting the scissor gear assembly in the gear train easier. With the additional connection means both ends of the spring can be connected either to the main gear or to the auxiliary gear so the spring(s) are partial pre-loaded. This way the scissor gear assembly can be easily assembled and transported before it is placed in a gear train meshing with a counter gear.
  • An optional grenade pin can be used to fix the relative gear position while aligning the gear teeth of the main gear with the auxiliary gear. This way the tooth gap needs not to be forced open during assembly of the scissor gear into the gear train.
  • the grenade pin can have an eccentric protrusion, so by rotation of the pin the auxiliary gear rotational position relative to the main gear can be fine adjusted. This way the tooth from main gear and auxiliary gear can be perfectly aligned. While aligning the gear tooth of both gears one end of the spring will lose contact with the main gear. The spring force will be transferred through the pin back to the main gear. This way the gear can be easily assembled in the gear train. By rotating the eccentric pin the tooth gap between main and auxiliary gear will reduce and at a certain moment the spring load in connection with the auxiliary gear will be transferred from the auxiliary gear to the counter gear in contact with the coast flank of the counter gear.
  • the drive flank of the counter gear tooth in mesh will also come in contact with the main gear and transfer the spring load from the counter gear to the main gear back to the other end of the spring. At this point the load transfer via the pin will disappear and the pin can be easily pull out of the main gear.
  • the eccentric grenade pin can be also a tool only used at the gear train assembly line to temporally align the gear teeth of main gear and auxiliary gear during mounting of the scissor gear assembly.
  • the angle over which the interruption in the annular spring and/or further spring extends is preferably less than 90°.
  • FIG. 1 shows an example of a scissor gear assembly in perspective view
  • FIG. 2 shows the scissor gear assembly in exploded view
  • FIG. 3 shows the scissor gear assembly in front view.
  • FIG. 4 shows an embodiment of the scissor gear assembly according to the invention in perspective view
  • FIG. 5 shows the scissor gear assembly of FIG. 4 in exploded view
  • FIG. 6 shows the scissor gear assembly of FIG. 4 in front view.
  • FIGS. 1 to 3 an example of a scissor gear assembly is shown in a perspective view, an exploded view and in a front view respectively.
  • the scissor gear assembly 1 has a main gear 3 and auxiliary gear 5 concentric to the main gear and in axial direction near the main gear. Further, the assembly has multiple planar annular springs 7 being interrupted at one place. At the interruption the springs have two ends 7 a and 7 b .
  • the springs are present between both gears and are arranged within the circumference of the main gear.
  • the springs are with one end 7 a connected to the main gear 3 and with the other end 7 b to the auxiliary gear 5 , so that both gears are connected to each other in rotation direction via the springs.
  • These connections are realized by pins on the ends 7 a , 7 b of the springs and corresponding holes in the gears 3 , 5 in which the pins protrude.
  • the main gear 3 and the auxiliary gear 5 both have a central opening 11 , 13 . Further, the main gear is provided with a collar 15 around the opening 11 , which collar protrudes through the opening 13 in the auxiliary gear. The diameter of the opening 13 is slightly larger than that of the collar, so that the auxiliary gear 5 , can rotate around the collar 15 .
  • the auxiliary gear 5 is fixed in axial direction on the collar 15 by a retaining ring 17 which is locked in a circumferential groove present in the collar.
  • Each spring 7 substantially encloses a surface 9 .
  • the rotation axis 4 of the main gear is present outside these surfaces 9 within the planar annular springs 7 . Because the rotation axis is completely outside the circumference of the spring, space is provided for multiple annular springs and holes 19 for bolds. Further, viewed in axial direction the central hole 11 in the main gear 3 and the surfaces 9 within the planar annular springs do not overlap each other.
  • Cylindrical cavities 21 are provided in the main gear to incorporate the annular springs.
  • the diameter of these cavities are slightly smaller than the outer diameter of the annular springs 7 in relaxed condition.
  • the springs are assembled in sprung load condition with a stroke that is just a little bit smaller than the stroke in operating condition when the gear assembly 1 is in mesh with its counter gear.
  • a grenade pin 23 is present in a hole 25 in the main gear 3 and protrudes through a hole 27 in the auxiliary gear 5 to fix the relative position of both gears.
  • the grenade pin has an eccentric protrusion 29 present in the hole 25 , so that by turning the pin 23 the relative angular position of the auxiliary gear and the main gear can be adjusted.
  • Such a grenade pin can also be used in the assembly shown in FIGS. 4-6 .
  • the springs can be axial positioned between the main gear body and the auxiliary gear body.
  • a cavity can be provided in one of the gear bodies to incorporate the annular spring.
  • the cavity can be made cylindrical so it is easy to machine.
  • the cavity diameter can be made a little bit smaller than the outer diameter of the annular spring in relaxed condition.
  • the spring(s) can be assembled in sprung load condition with a stroke that is just a little bit smaller than the stroke in operating condition when the gear is in mesh with its counter gear. This is one option forming the additional connection means of the spring end.
  • auxiliary pins need to be sufficient smaller than the corresponding holes so the auxiliary pins can freely move when the scissor gear gets in mesh with its counter gear.
  • the auxiliary pins are integrally formed with the spring during the fine blanking process.
  • FIGS. 4 to 6 an embodiment of the scissor gear assembly is shown in a perspective view, an exploded view and in a front view respectively.
  • the scissor gear assembly 31 has a main gear 33 and auxiliary gear 35 concentric to the main gear and in axial direction near the main gear.
  • the assembly has multiple planar annular springs 37 being interrupted at one place.
  • the main gear 33 has a circular collar 38 which is in contact with the inner surface of the toothed ring.
  • the collar is interrupted at locations where the springs extend inside the toothed ring.
  • the hooks 38 a , 28 b are part of the side walls of the collar 38 bounding the interruptions.
  • the springs 37 each have a shape of a half circle. At the ends of the half circle there are arms extending in radial direction towards the middle of the circle. The angle over which the interruptions in the annular springs extend is less than 90°. At the interruption the springs have two ends 37 a and 37 b . These springs 37 are integrally formed with the auxiliary gear 35 and are with one end 37 b fixed to the auxiliary gear 35 and the other free ends 37 a are in contact with ends 38 a of further collars 38 on the main gear 33 . These ends 38 a constitute hooks behind which the ends 37 a of the spring 37 are caught in axial direction. The other ends 38 b of the collars 38 constitute further hooks behind which the other ends 37 b are caught in axial direction.
  • the main gear 33 has a central opening 41 and each spring 37 substantially encloses a surface 39 . Viewed in axial direction the rotation axis 34 of the main gear is present outside these surfaces 39 . Because the rotation axis is completely outside the circumference of the spring, space is provided for multiple annular springs and holes 43 . Further, also in this assembly, viewed in axial direction the central hole 41 in the main gear 33 and the surfaces 39 within the planar annular springs do not overlap each other.
  • a grenade pin 45 is present in a hole 47 in the main gear 33 and protrudes through the auxiliary gear 35 wherein it contacts a side wall of the end 37 b of one of the spring 37 to fix the relative position of both gears. Also this grenade pin has an eccentric protrusion 49 present in the hole 47 , so that by turning the pin 45 the relative angular position of the auxiliary gear and the main gear can be adjusted.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
US15/745,767 2015-07-18 2016-07-18 Scissor gear assembly Active US10520074B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
NL2015189A NL2015189B1 (en) 2015-07-18 2015-07-18 Scissor gear assembly.
NL2015189 2015-07-18
PCT/EP2016/067100 WO2017013082A1 (en) 2015-07-18 2016-07-18 Scissor gear assembly

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US20180216716A1 US20180216716A1 (en) 2018-08-02
US10520074B2 true US10520074B2 (en) 2019-12-31

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US (1) US10520074B2 (de)
EP (1) EP3325849B1 (de)
NL (1) NL2015189B1 (de)
WO (1) WO2017013082A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11407436B2 (en) * 2019-03-04 2022-08-09 Byton North America Corporation Steering wheel with fixed center

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2547035B (en) * 2016-02-05 2019-03-13 Ford Global Tech Llc Gear assembly
US10767732B2 (en) 2017-08-22 2020-09-08 Ecolab Usa Inc. Eccentric gear drive with reduced backlash
DE102017126205A1 (de) * 2017-11-09 2019-05-09 Man Truck & Bus Ag Zahnrad, insbesondere Zwischenrad, für einen Rädertrieb
CN108317234B (zh) * 2018-04-12 2023-08-04 常州机电职业技术学院 具有消隙功能的直齿圆柱齿轮
WO2022087555A1 (en) * 2020-10-21 2022-04-28 Cummins Inc. Centrifugal anti-backlash scissor gear

Citations (14)

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Publication number Priority date Publication date Assignee Title
US4947707A (en) * 1987-10-19 1990-08-14 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Arrangement for decoupling the torsional vibrations in a gear transmission
US5870928A (en) * 1997-05-08 1999-02-16 Cummins Engine Company, Inc. Anti-lash gear with alignment device
US6109129A (en) * 1997-05-08 2000-08-29 Cummins Engine Company, Inc. Apparatus and method for adjusting a gear
US20020121152A1 (en) * 2001-03-05 2002-09-05 White David C. Phased gear set comprised of a pair of phased gears
US20020128098A1 (en) * 2001-03-05 2002-09-12 Mott Philip J. Self-tensioning sprocket for power transmission chain
WO2008142131A2 (en) * 2007-05-21 2008-11-27 Vcst Industrial Products Split gear for avoiding backlash when engaging a mating gear
US20090114045A1 (en) * 2007-11-01 2009-05-07 Brian Wilson Power Take-Off Unit Having Scissor Gears
US20100139431A1 (en) * 2008-12-05 2010-06-10 Kia Motors Corporation Scissors gear
DE102011115692A1 (de) * 2011-10-12 2013-04-18 Werner M. Bless Gezahntes Bauteil
US20130145878A1 (en) * 2011-12-08 2013-06-13 Kia Motors Corporation Scissors gear structure and manufacturing method thereof
US20130213168A1 (en) * 2010-09-29 2013-08-22 Miba Sinter Austria Gmbh Toothed wheel arrangement and method for producing a bayonet fastening
US20140116174A1 (en) * 2012-10-25 2014-05-01 Miba Sinter Austria Gmbh Gear system
US20140360300A1 (en) * 2013-06-11 2014-12-11 Miba Sinter Austria Gmbh Gear arrangement
US20160053881A1 (en) * 2012-12-28 2016-02-25 Gkn Sinter Metal Holding Gmbh Divided toothed wheel

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Publication number Priority date Publication date Assignee Title
DE7515665U (de) * 1975-09-25 Dau P & Co Zahnradantrieb
AT413748B (de) * 2004-03-22 2006-05-15 Miba Sinter Austria Gmbh Zahnrad für eine spielfreie stirnradstufe
AT511812B1 (de) * 2011-12-02 2013-03-15 Miba Sinter Austria Gmbh Zahnrad für eine spielfreie stirnradstufe

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4947707A (en) * 1987-10-19 1990-08-14 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Arrangement for decoupling the torsional vibrations in a gear transmission
US5870928A (en) * 1997-05-08 1999-02-16 Cummins Engine Company, Inc. Anti-lash gear with alignment device
US6109129A (en) * 1997-05-08 2000-08-29 Cummins Engine Company, Inc. Apparatus and method for adjusting a gear
US20020121152A1 (en) * 2001-03-05 2002-09-05 White David C. Phased gear set comprised of a pair of phased gears
US20020128098A1 (en) * 2001-03-05 2002-09-12 Mott Philip J. Self-tensioning sprocket for power transmission chain
WO2008142131A2 (en) * 2007-05-21 2008-11-27 Vcst Industrial Products Split gear for avoiding backlash when engaging a mating gear
US20090114045A1 (en) * 2007-11-01 2009-05-07 Brian Wilson Power Take-Off Unit Having Scissor Gears
US20100139431A1 (en) * 2008-12-05 2010-06-10 Kia Motors Corporation Scissors gear
US20130213168A1 (en) * 2010-09-29 2013-08-22 Miba Sinter Austria Gmbh Toothed wheel arrangement and method for producing a bayonet fastening
DE102011115692A1 (de) * 2011-10-12 2013-04-18 Werner M. Bless Gezahntes Bauteil
US20130145878A1 (en) * 2011-12-08 2013-06-13 Kia Motors Corporation Scissors gear structure and manufacturing method thereof
US20140116174A1 (en) * 2012-10-25 2014-05-01 Miba Sinter Austria Gmbh Gear system
US20160053881A1 (en) * 2012-12-28 2016-02-25 Gkn Sinter Metal Holding Gmbh Divided toothed wheel
US20140360300A1 (en) * 2013-06-11 2014-12-11 Miba Sinter Austria Gmbh Gear arrangement

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11407436B2 (en) * 2019-03-04 2022-08-09 Byton North America Corporation Steering wheel with fixed center

Also Published As

Publication number Publication date
US20180216716A1 (en) 2018-08-02
EP3325849A1 (de) 2018-05-30
EP3325849B1 (de) 2022-03-09
WO2017013082A1 (en) 2017-01-26
NL2015189B1 (en) 2017-02-07

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